Self-propelled loader



' sept 12, 1967 J, L JUHL'ET A L 3,340,942

SELF-PROPELLED LOADER Filed Aug. 2o, 1965 v 5 sheets-sheet 1 Ch NTOR/iff sept. 12, w67- J. L. JUHL' ET AL SELF-PROPELLED LOADER FiledAug. 2o, 1965 5 Sheets-Sheet 2 Sept. 12, 1967' -J. L.. JUHL ET AL SELF-PROPELLED LC )ADER 5 Sheets-Sheet 3 Filed Aug. 20, 1965 United StatesPatent O 3,340,942 SELF-PROPELLED LOADER James L. .luhl and Lyle H.Tufty, Hudson, Iowa, assignors to Universal Manufacturing Company,Hudson, Iowa, a corporation of Iowa Filed Aug. 20, 1965, Ser. No.481,217 9 Claims. (Cl. 180-6.66)

ABSTRACT OF THE DISCLOSURE A self-propelled vehicle comprising, a framemeans, first and second pairs of wheels on opposite sides of the framemeans and a power means adapted to selectively rotate said first andsecond pair of Wheels in forwardly or rearwardly directions.

This is a continuation-in-part application of the application, Ser. No,468,684, tiled July 1, 1965.

This invention relates to a loader device and more particularly to aself-propelled loader.

Conventional loaders of the front-end type are rather large anddifficult to maneuver in small spaces. Additionally, a conventionalloader has a large number of controls such as levers, foot pedals, etc.which makes it difficult for the operator to efficiently operate thedevice.

Therefore, it is a principal object of this invention to provide acompact, self-propelled loader which can be maneuvered in a minimumamount of space.

A further object of this invention is to provide a selfpropelled loaderwherein the steering of the loader is accomplished by the utilization oftwo control levers.

A further object of this invention is to provide a loader which has aclutch mechanism associated therewith which is eflicient andtrouble-free.

A further object of this invention is to provide a loader which issimple in design, economical of manufacture and refined in appearance.

These and other objects will be apparent to those skilled in the art.

This invention consists in the construction, arrangements, andcombination of the various parts of the device, whereby the objectscontemplated are attained as hereinafter more fully set forth,specifically pointed out in the-claims, and illustrated in theaccompanying drawings in which:

FIG. 1 is a sectional view of the device as seen on line 1-1 of FIG. 7with the chains removed to more fully illustrate the invention;

FIG. 2 is a side elevational View of the clutches seen in FIG. 1;

FIG. 3 is a sectional View of the rear clutch seen on line 3-3 of FIG. 2at an enlarged scale;

FIG. 4 is a side elevational View of the device as seen on line 4-4 ofFIG. 7;

FIG. 5 is a fragmentary, sectional view taken generally along line 5 5of FIG. 7 to illustrate the relationship of the cam members with respectto the movement of the control lever;

FIG. 6 is an exploded perspective view of one of the clutches of thedevice; and

FIG. 7 is a fragmentary perspective view of the loader device.

The numeral 10 generally designates the loader of this invention whichincludes a right side 11, left side 13, forward end 15, rearward end 17and boom means 19. As seen in FIG. 1, side 11 is comprised of an innerpanel member 21 and an outer panel member 22 spaced therefrom having anopening 23 formed therein which is detachably closed by panel member 25in any suitable manner. Side 13 is identical to side 11 'and for thatreason will not be described in detail.

ICC

Operatively secured to side 11 is a front clutch 27 and a rea-r clutch29. Clutches identical to clutches 27 and 29 are provided on the leftside of the loader as well and will not be described in detail.

Clutch 29 includes a bolt member 31 which extends outwardly throughpanel member 21 and which is embraced by a splined hub 33 having anexternally threaded outer end and a sprocket 35 secured thereto bywelding or the like adjacent its inner end. As best seen in FIG. 3, thespacer 37 embraces hub 33 outwardly of sprocket 3S and is positionedinwardly of a bearing 39 having an inner race 41 and an outer race 43.Embracing outer race 43 is a drive cup 45 having a base portion 47 and aflange portion 49 extending outwardly therefrom. As best seen in FIG. 6,flange portion 49 is provided with a plurality of notches 51 formedtherein. Drive cup 45 is prevented from moving inwardly with respect tosprocket 35 by means of snap ring 53 engaging outer race 43 of bearing39. A backing plate 54 is received by drive cup 45 and embraces outerrace 43 of bearing 39 as best seen in FIG. 3. A sprocket 55 is mountedon drive cup 45 (FIGS. 3 and 6) and is secured thereto by welding or thelike.

A plurality of friction discs 57 having a plurality of tab portions 59extending therefrom which are received by the notches 51 in drive cup 45embrace hub 33 as seen in FIG. 3. Friction discs 57 are separated fromeach other by a separator disc 61 positioned between each adjacent pairof friction discs. Separator discs 61 have a plurality of tab portionsy63 extending from its inside diameter which are splined onto hub 33. Arelease spring 65 embraces hub 33 outwardly of bearing 39 and has itsinside diameter engaging inner race 41 and its outside diameter engagingthe innermost separator disc 61. As

'F seen in FIG. 3, a pair of opposing release springs 65 are positionedbetween each adjacent pair of separator discs. A pressure plate 67 issplined onto hub 33 and is received by drive cup 45 and engages theoutermost friction disc 57. A pair of release springs 65 are positionedbetween the -outermost separator disc and the inner surface of pressureplate 67.

Embracing hub 33 outwardly of pressure plate 67 is an inner cam bearing69 having inner and outer races and is axially movable on hub 33 to movepressure plate 67 inwardly with respect to drive cup 45. An inner cammember 71 embraces inner cam bearing 69 and is prevented from inwardmovement with respect to cam bearl ing 69 by means of snap ring 73. Asseen in FIG. 6, cam

member 71 is cup shaped and has a plurality of tapered cam surfaces 73formed therein. Cam member 71 is provided with a tab member 75 securedthereto by welding or the like which extends downwardly therefrom. An

i outer cam bearing 77 embraces hub 33 and has inner and outer races. Anouter cam member 79 embraces cam bearing 77 and is prevented fromoutward movement with respect to cam bearing 77 by means of snap ring81. Outer cam member 79 is identical to cam member 71 and has aplurality of tapered cam surfaces 83 formed therein. Although cammembers 71 and 79 are identical, they are positioned in an oppositelyfacing relationship so that the cam surfaces 73 and S3 form pairs ofcomplimentary and oppositely facing cam surfaces into which are mountedballs 85. Cam member 79 is provided with a tab member 87 secured theretoby welding or the like which extends upwardly therefrom. It can beappreciated that because of the complimentary and oppositely facing cam,

member 71 causes inner cam bearing 69 to move against pressure plae 61to move pressure plate 61 axially inwardly on hub 33 thereby overcomingthe resistance of the -release springs 65 and causing the friction discs57 to frictionally engage the separator discs 61. A clutch adjustingrcollar 89 is threadably mounted on the outer end of hub 33 (FIG. 3) andis maintained thereon by means of set screw 91.

As stated before, front clutch 27 is identical to rear clutch 29 andwill not be described in detail but structure on front clutch 27corresponding to structure on 29 will be indicated by Front clutch 27 ispositioned on the loader so that tab portion 87 on outer cam member 79extends downwardly rather than upwardly and tab portion 75 `on inner cammember 71' extends upwardly rather than downwardly. Tab members 37 and75' are pivotally interconnected by arm member 93y while tab members 75and 87 are pivotally interconnected by means of arm member 95. A righthand control lever 97 is pivotally connected to loader and has a shaft99 extending outwardly through panel member 21 which is rotated uponpivotal movement of control lever 97 An arm 'member 101 is rigidlysecured to shaft 99 by any con venient means and extends downwardlytherefrom and has a turnbuckle means 103 .pivotally connected to itslower end. A bolt member 105 extends between panel member 21 and 23 andhas a sleeve 107 rotatably mounted thereon. A U-shaped arm member 109 isrigidly secured to sleeve 107 and extends upwardly therefrom and ispivotally connected to the forward end of turnbuckle 103. Arm members111 and 1-13 are pivotally connected to the forward ends of arm members93 and 95 respectively. The forward ends of arm members 111 and 113 arepivotally connected to the upper end of arm 109.

FIG. 4 illustrates the arrangement of the various chains on the rightside of the loader and will now be described in detail. A jack shaft1.15 rotatably extends outwardly through channel member 21 and has asprocket '117 mounted on its outer end. Jack shaft 115 is' operativelyconnected to the loader power means. A chain 119 extends around sprocket117, sprocket 55 on rear clutch 29 and sprocket 55 on front clutch 27. Aconventional chain tightener 121 is secured to panel member 21 andoperatively engages chain 119. A shaft 123 rotatably extends outwardlythrough panel 21 and has a small outer sprocket 125 operatively mountedthereon. Sprocket 125 has a front axle drive chain 127 extendingtherearound which embraces a front axle drive sprocket 129 operativelymounted on front axle 131. Front axle 131 has a wheel member 133operatively mounted thereon. Shaft 73 is also provided with a largeintermediate sprocket 135 and a small inner sprocket 137. Sprocket 137has a rear axle drive chain 139 extending therearound which alsoembraces a rear axle drive sprocket 141 mounted on rear axle 143. Awheel member 145 is operatively mounted on rear axle 143. As best seenin FIG. 4, a chain 147 eX- tends around sprocket 135, around sprocket149 of chain tightener assembly 151, around the lower end of sprocket 35and around the upper and rearward end of sprocket 35.

Each side of loader 10 is provided with a front clutch assembly and rearclutch assembly and their associated mechanism and for that reason hasnot been shown. A left hand control lever 153 is operatively connectedto a rear clutch assembly and a front clutch assembly corresponding torear clutch assembly 29 and front clutch assembly 27 respectively.

The normal method of operation is as follows. Loader 10 is movedforwardly by moving one or both of control levers 97 and 153 forwardlyfrom their neutral position. FIG. 4 illustrates the forward and rearwardmovement of lever 97 with respect to its neutral position shown in fulllines. The uppermost drawing in FIG. 5 illustrates the relationshipbetween .the inner and outer cam members in the rear and front clutchwhen the control lever 97 is in its neutral position. It can be seenfrom the uppermost drawing in FIG. 5 that ball 85 in rear clutch 29 isapproximately in the center of the length of the tapered cam surfaces 73and 83. Likewise in the front clutch 27, ball is substantially in thecenter of the length of cam surfaces 73' and 83. The center drawing inFIG. 5 illustrates the position of the inner end outer cam members inthe rear and front clutches when the control lever 97 is. movedforwardly. It can be seen that inner cam member 71 in rear clutch 29 hasbeen moved away from outer cam member 79 or in an inwardly directionwhile inner cam member 71 has been moved towards outer cam member 79 orin an outwardly direction. Inner cam member 71 in rear clutch 29 iscaused to be moved inwardly due to the shallow por-tions of thecomplementary cam surfaces 73 and l83 being directly opposite eachother. Inner cam member 7.1 in front clutch 27 is permitted to movetowards outer cam member 79 because the deep portions of thecomplementary cam surfaces 73 and 83 being directly opposite each other.Inner cam mem-ber 71 is yieldably urged outwardly due to the action ofthe release spring 65. The lowermost drawing in FIG. 5 illustrates therelationships between the inner and outer cam members in rear clutch 29and front clutch 27 when control lever 97 has been moved rearwardly. Itcan be seen that the relationship between the cam members in the rearand front clutches has been reversed from the relationship shown in thecenter drawing in FIG. 5.

As viewed in FIG. 4, jack shaft will cause rotation of sprocket 117 in aclockwise direction which also imparts clockwise rotation of sprocket 55in rear clutch 29 and sprocket 55 in front clutch 27 regardless of theposition of control lever 97. When control lever 97 is in its neutralposition, the inner and outer cam members in rear clutch 29 and frontclutch 27 will assume the relationship illustrated in the top drawing inFIG. 5. When the inner and outer cam members occupy this relationship,the pressure plate 67 is not urged into engagement with the outermostfriction disc 57. The rotation of sprocket 55 also causes rotation ofdrive cup 45 which in turn causes rotation of the friction discs 67.Because pressure plate 67 is not bearing against the outermost frictiondisc 57, there is no frictional engagement between the friction disc 57and the separator discs 61 which permits rotation of the friction discs57 without impar-ting rotation to the separator discs 61 which meansthat sprocket 55 is rotated while sprocket 35 remains in a stationaryposition. Front clutch 27 is in an identical position to rear clutch 29so that sprocket 55 is rotating while sprocket 35 is in a stationaryposition.

When control lever 97 is moved forwardly, inner cam member 71 and outercam member 79 are rotated in opposite directions with respect to eachother due to the various arm members, tab members, etc., which connectsthem to control lever 97. The forward movement of control lever 97causes outer cam member 79 to be rotated in a counterclockwise directionand causes inner cam member 71 to be rotated in a clockwise direction asviewed 1n FIG. 2. The forward movement of control lever 97 causes outercam member 79 in front clutch 27 to be rotated in a clockwise directionand causes inner cam member 71 to be rotated in a counterclockwisedirection as viewed in FIG. 2. When control lever 97 is moved forwardly,the shallow portions of the complementary and oppositely facing camsurfaces 73 and 83 in rear clutch 29 are caused to be positionedopposite each other so that ball 85 causes inner cam member 71 to bemoved inwardly with respect to outer cam member 79. The inward movementof inner cam member 71 causes inner cam bearing 69 to lbe moved againstpressure plate 67 and to move pressure plate 67 inwardly against theoutermost friction disc 57. The inward movement of pressure plate 67causesthe friction discs 57 to frictionally engage the separator discs61. The frictional engagement between friction discs 57 and separatordiscs 61 causes the rotating friction discs 57 to cause separator discs61 to be also rotated. The rotation of separator discs |61 causes hub 33to be rotated due to the splined engagement between separator discs 61and hub 33.,The rotation of hub 33 causes sprocket -35 to be rotatedwhich causes sprocket 135 to be rotated in a clockwise direction whichimparts clockwise rotation to sprockets 129 and 141 as viewed in FIG. 4.The clockwise rotation of sprockets 129 and 143 imparts a forwardrotational movement to wheels 133 and 145 respectively. When the controllever 97 has been moved, to its forward position and sprocket 35 hasbeen causedv to be rotated in a clockwise direction as viewed in FIG. 4,sprocket 35 will be freely rotating in la counterclockwise directionwithout causing any internal wear of the friction discs and separatordiscs in the front clutch.

The rearward movement of control lever 97 causes inner cam member 71 tobe moved inwardly with respect to outer cam member 79 in front clutch 27while inner cam member 71 has been moved toward outer cam member 79 inrear clutch 29. The inward movement of inner cam member 71 with -respectto outer'cam member 79 causes sprocket 35 to be rotated in a clockwisedirection which causes sprocket 135 to be rotated in a counterclockwisedirection as viewed in FIG. 4 to cause wheels 145 and 133 to be rotatedin a counterclockwise direction as viewed in FIG. 7 to impart rearwoodmovement to the loader 10. During the time that sprocket 35 is impartingrearward movement to loader 10, sprocket 35 in rear clutch 29 is looselyfreely rotating without causing internal wear in the clutch. Thus it canbe seen that forward movement of control lever 97 causes rear clutch 29to propel loader 10 forwardly while the rearward movement of controllever 97 causes front clutch 27 to propel the loader 10 rearwardly.

When both of control levers 97 and 153 are moved forwardly, the rearclutches at each of the sides of loader 10 will be moving the wheels ateach side thereof in a forwardly rotational movement while the rearwardmovement of both of control levers 97 and 153 will cause the frontclutches at each of the sides of loader 10 to rotate the wheels at eachside thereof in a rearwardly rotational movement. If desired, one of thecontrol levers may be moved forwardly while the other control lever ismoved rearwardly which causes the wheels on one side of the loader to berotated in one direction while the wheels at the other side of theloader will be caused to rotate in an opposite direction to permit theloader to scrub around in its own tracks so that it may be turned in aminimum amount of space.

Thus it can be seen that an efficient clutch mechanism for a loaderdevice has been provided which is not subject to extreme wear and whichpermits the loader to be operated in a minimum amount of space.

Thus it can be seen that the device accomplishes at least all of itsstated objectives.

Some changes may be made in the construction and arrangement of ourself-propelled loader without departing from the real spirit and purposeof our invention, and it is our intention to cover by our claims, anymodified forms of structure or use of mechanical equivalents which maybe reasonably included within their scope.

We claim:

1. In a loader having opposite sides,

a power means on said loader,

first and second clutch means on one side of said loader and beingoperatively connected to a first pair of wheels on said one side,

third and fourth clutch means on the other side of said loader and beingoperatively connected to a second pair of wheels on said other side,

said first and third 4clutch means being operatively connected to saidpower means and adapted to cause rotation of said first and second pairof wheels respectively in one direction at times,

said second and fourth clutch means being operatively connected to saidpower means and adapted to cause rotation of said first and second pairof wheels respectively in a second direction at times,

a first control means operatively connected to said first and secondclutch means to selectively cause rotation of said first pair of wheelsin said one direction at times and to cause rotation of said first pairof wheels in said second direction at times,

a second control means operatively connected to said third and fourthclutch means to selectively cause rotation of said second pair of wheelsin said one direction at times and to cause rotation of said second pairof wheels in said second direction at times,

each of said rst, second, third and fourth clutches including, arotatable hub having inner and outer ends; said hub having at least oneexternal axial groove formed therein and having a first drivetransmitting means rigidly mounted thereon adjacent the inner end, adrive cup rotatably mounted on said hub outwardly of said first drivetransmitting means and having a flange portion having at least one slotformed therein, a second drive transmitting means rigidly mounted onsaid drive cup, a plurality of friction discs rotatably mounted on saidhub outwardly of said drive cup, each of said friction discs having atleast one tab member extending therefrom in engagement with said slot, aseparator disc between each adjacent friction disc, each of saidseparator discs being splined into said groove in said hub for rotationtherewith, said friction discs having a larger inside diameter than saidseparator discs, a plurality of release springs operatively mounted onsaid hub maintaining said separator discs out of frictional engagementwith said friction discs, a pressure plate splined into said groove insaid hub outwardly of said friction discs and said separator discs, saidpressure plate being axially movable on said hub, a first cam bearingrotatably mounted on said hub outwardly of said pressure plate and4being axially movable thereon to axially move said pressure plateinwardly on said hub, a first cam member rotatably mounted on said firstcam bearing, a second cam bearing rotatably mounted on said huboutwardly of said first cam bearing, a second cam member rotatablymounted on said second cam bearing, said first and second cam membershaving cam surfaces formed therein forming pairs of complementary andoppositely facing cam surfaces, a ball between and in engagement witheach pair of oppositely facing cam surfaces whereby rotation of saidfirst and second cam members in one direction with respect to each othercauses the balls to ride along their respective surfaces and separatesaid first and second cam members and causes inward axial movement ofsaid first cam member with respect to said hub, said inward axialmovement of said first cam member causing said iirst cam bearing to movesaid pressure plate axially inwardly on said hub thereby overcoming theresistance of said release springs and causing said friction discs tofrictionally engage said separator discs, said frictional engagement ofsaid friction discs with said separator discs causing said first drivetransmitting means to be rotated when rotational power is being suppliedto said second drive transmitting means and causing said second drivetransmitting means to be rotated when rotational power is supplied tosaid first drive transmitting means, said first control means beingoperatively connected to said -first and second cam members in each ofsaid first and second clutches to effect rotation thereof at times andincluding first and second tabs secured to said first and second cammembers respectively in said first clutch, third and fourth tabs securedto said first and second cam members respectively in said second clutch,a first linkage ieans interconnecting said first tab and said fourthtab, a second linkage means interconnecting said second tab and saidthird tab, a third linkage means interconnecting said first and secondlinkage means to a first control lever.

2. In a loader having opposite sides,

a power means on said loader,

first and second clutch means on one side of said loader and beingoperatively connected to a first pair of wheels on said one side,

third and fourth clutch means on the other side of said loader and beingoperatively connected to a second pair of Wheels on said other side,said first and third clutch means being operatively connected to saidpower means and adapted to cause rotation of said first and second pairof wheels respectively in one direction at times,

said second and fourth clutch means being operatively connected to saidpower means and adapted to cause rotation of said first and second pairof Wheels respectively in a second direction at times,

a first control means operatively connected to said first and secondclutch means to selectively cause rotation of said first pair of wheelsin said one direction at times and to cause rotation of said first pairof wheels in said second direction at times,

a second control means operatively connected to said third and fourthclutch means to selectively cause rotation of said second pair of Wheelsin said one direction at times and to cause rotation of said second pairof wheels in said second direction at times,

each of said first, second, third and fourth clutches including, arotatable hub having inner and outer ends; said hub having at least oneexternal axial groove formed therein and having a first drivetransmitting means rigidly mounted thereon adjacent the inner end, adrive cup rotatably mounted on said hub outwardly of said first drivetransmitting means and having a flange portion having at least one slotformed therein, a second drive transmitting means rigidly mounted onsaid drive cup, a plurality of friction discs rotatably mounted on saidhub outwardly of said drive Cup, each of said friction discs having atleast one tab member extending therefrom in engagement with said slot, aseparator disc between each adjacent friction disc, each of saidseparator disc being splined into said groove in said hub for rotationtherewith, said friction discs having a larger inside diameter than saidseparator discs, a plurality of release springs operatively mounted onsaid hub maintaining said separator discs out of frictional engagementwith said friction discs, a pressure plate splined into said groove insaid hub outwardly of said friction discs and said separator discs, saidpressure plate being axially movable on said hub, a first cam bearingrotatably mounted on said hub outwardly of said pressure plate and beingaxially movable thereon to axially move said pressure plate inwardly onsaid hub, a first cam member rotatably mounted on said first cambearing, a second cam bearing rotatably mounted on said hub outwardly ofsaid first cam bearing, a second cam member rotatably mounted on saidsecond cam bearing, said first and second cam members having camsurfaces formed therein forming pairs of complementary and oppositelyfacing cam surfaces, a ball between and in engagement with each pair Iofoppositely facing cam surfaces whereby rotation of said first and secondcam members in one direction with respect to each other causes the ballsto ride along their respective surfaces and separate said first andsecond cam members and causes inward axial movement of said first cammember with CII respect to said hub, said inward axial movement of saidfirst cam member causing said first cam bearing to move said pressureplate axially inwardly on said hub thereby overcoming the resistance ofsaid release springs and causing said friction discs to frictionallyengage said separator discs, said frictional engagement of said frictiondiscs with said separator discs causing said first drive transmittingmeans to be rotated when rotational power is being supplied to saidsecond drive transmitting means and causing said second drivetransmitting means to be rotated when rotational power is supplied tosaid first drive transmitting means, said second control means beingoperatively connected to said first and second cam members in each ofsaid third and fourth clutches to effect rotation thereof at times andincluding first and second tabs secured to said first and second cammembers in said third clutch, third and fourth tabs secured to saidfirst and second cam members in said fourth clutch, a first linkagemeans interconnecting said first tab and said fourth tab, a secondlinkage means interconnecting said second tab and said third tab, athird linkage means interconnecting said first and second linkage meansto a second control lever.

3. In a loader having opposite sides,

a power means on said loader,

first and second clutch means on one side of said loader and beingoperatively connected to a first pair of wheels on said one side,

third and fourth clutch means on the other side of said loader and beingoperatively connected to a second pair of wheels on said other side,

said first and third clutch means being operatively connected to saidpower means and adapted to cause rotation of said first and second pairof wheels respectively in one direction at times,

said second and fourth clutch means being operatively connected to saidpower means and adapted to cause rotation of said first and second pairof wheels respectively in a second direction at times,

a first control means operatively connected to said first and secondclutch means to selectively cause rotation of said first pair of wheelsin said one direction at times and to cause rotation of said first pairof wheels in said second direction at times,

a second control means operatively connected to said third and fourthclutch means to selectively cause rotation of said second pair of wheelsin said one direction at times and to cause rotation of said second pairof Wheels in said second direction at times,

each of said first, second, third and fourth clutches including arotatable hub having opposite ends, a first drive transmitting meansrigidly mounted on said hub adjacent one end for rotation therewith, asecond drive transmitting means rotatably mounted on said hub, aplurality of friction discs embracing said hub and secured to saidsecond drive transmitting means for rotation therewith, ayseparator discembracing said hub between each pair of friction discs, said separatordiscs being secured to said hub for rotation therewith, a pressure platemeans rotatably and axially movably mounted on said hub laterally ofsaid discs and being axially movable thereagainst at times to cause saidfriction discs to frictionally engage said separator discs whereby saidsecond drive transmitting means will be rotated when rotational power isapplied to said first drive transmitting means and whereby said firstdrive transmitting means will be rotated when rotational power isapplied to said second drive transmitting means, a roller cam meansrotatably mounted on said hub adapted to cause said pressure plate toaxially move against said discs at times, said roller cam meansincluding first and second cam members rotatably mounted on said hubmeans, said second cam member being axially movable on said hub means tocause said pressure plate to axially move against said discs, said cammembers each having cam surfaces forming pairs of complementary andoppositely facing cam surfaces, a 'ball -between and in engagement witheach pair of oppositely facing cam surfaces whereby rotation of saidfirst and second cam members in one direction with respect to each othercauses the balls to ride along their respective surfaces and separatesaid first and second cam members and causes said pressure plate to moveagainst said discs, Y

a first linkage means connecting one of said first and second cammembers of said first clutch with one of said first and second cammembers of said second clutch,

a second linkage means connecting the other of said first and second cammembers of said first clutch with the other of said first and second cammembers of said second clutch,

a third linkage means movable in two directions and connecting saidfirst and second linkage means with said first control means wherebymovement of said third linkage means in one direction will cause thediscs in said first clutch to be frictionally engaged and will cause thediscs in said second clutch to be frictionally disengaged, and-wherebymovement of said third linkage means in said second direction will causethe discs in said first clutch to be frictionally disengaged and willcause the discs in said second clutch to Ibe frictionally engaged,

a fourth linkage means connecting one of said first and second cammembers of said third clutch with one of said first and second cammembers of said fourth clutch,

a fifth linkage means connecting the other of said first and second cammembers with the other of said first and second cam members of saidfourth clutch,

a sixth linkage means movable in two directions and connecting saidfourth and fifth linkage means with said second control means wherebymovement of said sixth linkage means in one direction will cause thediscs in said third clutch to be frictionally engaged and will cause thediscs in said fourth clutch to be frictionally disengaged, and wherebymovement of said sixth linkage mea-ns in said second direction willcause the discs in said third clutch to be frictionally disengaged andwill cause the discs in said fourth clutch to be frictionally engaged.

4. The loader of claim 3 wherein said second drive transmitting means insaid first and second clutches are comprised of sprockets having a chainextending therearound which is driven by said power means, said firstdrive transmitter means in said first and second clutches comprised ofsprockets having a chain extending therearound, said chain extendingaround said first drive transmitting means being operatively connectedto said first pair of wheels, said second drive transmi-tting means insaid third and fourth clutches being comprised of sprockets having achain extending therearound which is driven by said power means, saidfirst drive transmitting means in said third and fourth clutchescomprised of sprockets having a chain extending the'rearound, said chainextending around said first drive transmitting means in said third andfourth clutches -being operatively connected to said second pair ofWheels.

5. In a loader having opposite sides,

a power means on said loader,

first and second clutch means on one side of said loader and beingoperatively connected to a first pair of wheels on said one side,

third and fourth clutch means on the other side lof said loader andbeing operatively connected to a second pair of wheels on said otherside,

said first and third clutch means being operatively connected to saidpower means and adapted to cause rotation of said first and second pairof Wheels respectively in one direction at times,

said second and fourth clutch means being operatively connected to saidpower means and adapted to cause rotation of said first and second pairof wheels respectively in a second direction at times,

a first control means operatively connected to said first and secondclutch means to selectively cause notation of said first pair of wheelsin said one direction at times and to cause rotation of said first pairof wheels in said second direction at times,

a second control means operatively connected to said third and fourthclutch means to selectively cause rotation of said second pair of wheelsin said one direction at times and to cause rotation of said sec- 4 ondpair of wheels in said second direction at times, each of said first,second, third and fourth clutches including, a rotatable hub havinginner and outer ends; said hub having at least one external axial grooveformed therein and having a first drive transmitting means rigidlymounted thereon adjacent the inner end, a drive cup rotatably mounted onsaid hub outwardly of said first drive transmitting means and having aflange portion having at least one slot formed therein, a second drivetransmitting means rigidly mounted on said drive cup, a plurality offriction discs rotatably 4mounted on said hub outwardly of said drivecup, each of said friction discs having at least one tab memberextending therefrom in engagement with said slot, a separator discbetween each adjacent friction disc, each of said separator discs beingsplined into said groove in said hub for rotation therewith, saidfriction discs having a larger inside diameter than'said separatordiscs, a plurality of release springs operatively mounted on said hubmaintaining said separator discs out of frictional engagement with saidfriction discs, a pressure plate splined into said groove in said huboutwardly of said friction discs and said separator discs, said pressureplate being axially movable on said hub, a first cam bearing rotatablymounted on said hub outwardly of said pressure plate and being.

axially movable thereon to axially move said pressure plate inwardly onsaid hub, a first cam member rotatably mounted on said first cambearing, a second cam bearing rotatably mounted on said hub outwardly ofsaid first cam bearing, a second cam member rotatably mounted on saidsecond cam bearing, said first and second cam members having camsurfaces formed therein forming pairs of complementary and oppositelyfacing cam surfaces, a ball between and in engagement with each pair ofoppositely facing cam surfaces whereby rotation of said first and secondcam members in one direction with respect to each other causes the ballsto ride along their respective surfaces and separate said first andsecond cam members and causes inward axial movement of said first cammember with respect to said hub, said inward axial movement of saidfirst cam member causing said first cam bearing to move said pressureplate axially inwardly on said hub thereby overcoming the resistance ofsaid release springs and causing said friction discs to frictionallyengage said separator discs, said frictional engagement of said frictiondiscs with said separator discs causing said first drive transmittingmeans to be rotated when rotational power is being supplied to saidsecond drive transmitting means and causing said second drivetransmitting means to. be rotated when rotational power is supplied tosaid first drive transmitting means.

6. The device of claim 5 wherein said first control means is operativelyconnected to said first and second cam members in each of said first andsecond clutches to effect rotation thereof at times.

7. The device of claim 5 wherein said first control means is operativelyconnected to said first and second cam members in each of said first andsecond clutches so that said first and second cam members in said firstclutch are rotated in said one direction as said first and second cammembers in said second clutch are rotated in an opposite direction.

8. The device of claim 5 wherein said second control means isoperatively connected to said first and second cam members in each ofsaid third and fourth clutches to effect rotation thereof at times.

9. The device of claim 5 wherein said second control means isoperatively connected to said third and fourth cam members so that saidfirst and second cam members in said third clutch are rotated in saidone direction as said first and second cam members in said fourth clutchare rotated in an opposite direction.

References Cited UNITED STATES PATENTS 1,470,078 10/1923 Hellvvarth74--361 X 1,680,553 8/1928 Krotz 180-6,66 3,011,608 12/1961 Hansen192-69 X 3,127,969 4/1964 Hansen 192-93 3,151,503 10/1964 Keller et al.3,231,117 1/1966 Melroe et al. 180-666 X LEO FRIAGLIA, Primary Examiner.

BENJAMIN HERSH, Examiner.

I. A. PEKAR, Assistant Examiner.

1. IN A LOADER HAVING OPPOSITE SIDES, A POWER MEANS ON SAID LOADER,FIRST AND SECOND CLUTCH MEANS ON ONE SIDE OF SAID LOADER AND BEINGOPERATIVELY CONNECTED TO A FIRST PAIR OF WHEELS ON SAID ONE SIDE, THIRDAND FOURTH CLUTCH MEANS ON THE OTHER SIDE OF SAID LOADER AND BEINGOPERATIVELY CONNECTED TO A SECOND PAIR OF WHEELS ON SAID OTHER SIDE,SAID FIRST AND THIRD CLUTCH MEANS BEING OPERATIVELY CONCONNECTED TO SAIDPOWER MEANS AND ADAPTED TO CAUSE ROTATION OF SAID FIRST AND SECOND PAIROF WHEELS RESPECTIVELY IN ONE DIRECTION AT TIMES, SAID SECOND AND FOURTHCLUTCH MEANS BEING OPERATIVELY CONNECTED TO SAID POWER MEANS AND ADAPTEDTO CAUSE ROTATION OF SAID FIRST AND SECOND PAIR OF WHEELS RESPECTIVELYIN A SECOND DIRECTION AT TIMES, A FIRST CONTROL MEANS OPERATIVELYCONNECTED TO SAID FIRST AND SECOND CLUTCH MEANS TO SELEVTIVELY CAUSEROTATION OF SAID FIRST PAIR OF WHEELS IN SAID ONE DIRECTION AT TIMES ANDTO CAUSE ROTATION OF SAID FIRST PAIR OF WHEELS IN SAID SECOND DIRECTIONAT TIMES, A SECOND CONTROL MEANS OPERATIVELY CONNECTED TO SAID THIRD ANDFOURTH CLUTCH MEANS TO SELECTIVELY CAUSE ROTATION OF SAID SECOND PAIR OFWHEELS IN SAID ONE DIRECTION AT TIMES AND TO CAUSE ROTATION OF SAIDSECOND PAIR OF WHEELS IN SAID SECOND DIRECTION AT TIMES, EACH OF SAIDFIRST, SECOND, THIRD AND FOURTH CLUTCHES INCLUDING, A ROTATABLE HUBHAVING INNER AND OUTER ENDS; SAID HUB HAVING AT LEAST ONE EXTERNAL AXIALGROOVE FORMED THEREIN AND HAVING A FIRST DRIVE TRANSMITTING MEANSRIGIDLY MOUNTED THEREON ADJACENT THE INNER END, A DRIVE CUP ROTATABLYMOUNTED ON SAID HUB OUTWARDLY OF SAID FIRST DRIVE TRANSMITTING MEANS ANDHAVING A FLANGE PORTION HAVING AT LEAST ONE SLOT FORMED THEREIN, ASECOND DRIVE TRANSMITTING MEANS RIGIDLY MOUNTED ON SAID DRIVE CUP, APLURALITY OF FRICTION DISCS ROTATABLY MOUNTED ON SAID HUB OUTWARDLY OFSAID DRIVE CUP, EACH OF SAID FRICTION DISCS HAVING AT LEAST ONE TABMEMBER EXTENDING THEREFROM IN ENGAGEMENT WITH SAID SLOT, A SEPARATORDISC BETWEEN EACH ADJACENT FRICTION DISC, ECH OF SAID SEPARATOR DISCSBEING SPLINED INTO SAID GROOVE IN SAID HUB FOR ROTATION THEREWITH, SAIDFRICTION DISCS HAVING A LARGER INSIDE DIAMETER THAN SAID SEPARATORDISCS, A PLURALITY OF RELEASE SPRINGS OPERATIVELY MOUNTED ON SAID HUBMAINTAINING SAID SEPARATOR DISCS OUT OF FRICTIONAL ENGAGEMENT WITH SAIDFRICTION DISCS, A PRESSURE PLATE SPLINED INTO SAID GROOVE IN SAID HUBOUTWARDLY OF SAID FRICTION DISCS AND SAID SEPARATOR DISCS, SAID PRESSUREPLATE BEING AXIALLY MOVABLE ON SAID HUB, A FIRST CAM BEARING ROTATABLYMOUNTED ON SAID HUB OUTWARDLY OF SAID PRESSURE PLATE AND BEING AXIALLYMOVABLE THERON TO AXIALLY MOVE SAID PRESSURE PLATE INWARDLY ON SAID HUB,A FIRST CAM MEMBER ROTATABLY MOUNTED ON SAID FIRST CAM BEARING, A SECONDCAM BEARING ROTATABLY MOUNTED ON SAID HUB OUTWARDLY OF SAID FIRST CAMBEARING, A SECOND CAM MEMBER ROTATABLY MOUNTED ON SAID SECOND CAMBEARING, SAID FIRST AND SECOND CAM MEMBERS HAVING CAM SURFACES FORMEDTHEREIN FORMING PAIRS OF COMPLEMENTARY AND OPPOSITELY FACING CAMSURFACES, A BALL BETWEEN AND IN ENGAGEMENT WITH EACH PAIR OF OPPOSITELYFACING CAM SURFCES WHEREBY ROTATION OF SAID FIRST AND SECOND